Vehicle cabin heating cooling and ventilation system

ABSTRACT

An air treatment system for a vehicle includes a first compressor selectively coupled to a first power source of the vehicle. A second compressor is selectively coupled to a second power source of the vehicle. A first heat exchanger communicating with an interior space is defined in the vehicle. A second heat exchanger communicates with an environment exterior to the vehicle. A valve member is provided which, in a first position, couples an inlet of each of the first and second compressors to an outlet of the first heat exchanger and an outlet of each of the first and second compressors to an inlet of the second heat exchanger. In a second position, the valve member couples the outlets of the first and second compressors to an inlet of the first heat exchanger and the inlets of each of the first and second compressors to an outlet of the second heat exchanger. A controller is provided that selectively actuates at least one of the first and second compressors and the valve member.

This application claims the benefit of U.S. Provisional Application Ser.No. 60/850,441 which was filed on Oct. 10, 2006.

FIELD OF THE INVENTION

The present invention relates to the field of tactical and non-tacticalvehicle cabin heating, nuclear chemical and biological (NBC) filteredand unfiltered air ventilation, and cooling systems. In particular, thepresent invention relates to systems intended to heat, cool, ventilate,or over pressurize the interior or crew compartment of a vehicle.

BACKGROUND OF THE INVENTION

The global war on terror has presented the military with new challenges.One such challenge is the redesign of combat vehicles to safely carrypersonnel and or cargo. One of the most important requirements for acombat vehicle's protection is counter mine design. These new mine/IEDprotected vehicles and armored fighting vehicles are designed foranti-personnel or larger anti-tank mines, armor penetrating andself-forged fragmented mines as well as improvised explosive devices(IEDs). To provide maximum protection new vehicles use special lowerframe V shapes to deflect a mine blast with increased armor and cleararmor windows for blast and bullet defense. Engines and transmissionsare also housed within armor. The only outside openings that can besafely opened are the firing ports located in the doors and side panels.This added ballistic protection of the engine, transmission, and crewcompartment has increased the cabin thermal load and mass therebysubstantially increasing the load on the heating, cooling, andventilation of the crew compartment.

Present tactical and non tactical vehicle heating and air conditioningsystems use two independent engine driven heat transfer fluid systems inorder to heat or cool the interior or cabin environment of a vehicle.Typically, in order to heat the interior, heated engine coolant iscirculated from the engine through a liquid-to-air type heat exchangerlocated in or near the interior of the vehicle. In order to cool theinterior, an engine driven compressor is typically used to compress arefrigerant. The condensed refrigerant is then allowed to pass through arefrigerant-to-air type heat exchanger (e.g. an evaporator coil) alsolocated in or near the interior. In addition, present vehicle airventilation systems may draw filtered or unfiltered air from the ambientenvironment.

There are several disadvantages in using such engine driven independentsystems for the heating and cooling of a vehicle interior. First, usingseparate heating and cooling systems requires the use of twice as manyfluid conduits and heat exchangers. In other words these independentsystems typically include one set of fluid conduits and an interior heatexchanger for heating and one set of fluid conduits and an interior heatexchanger for cooling. Having two sets of fluid lines and heatexchangers not only incurs additional expense in the manufacture of thevehicle, but also contributes to the overall vehicle weight andconsumption of valuable cabin space. This is particularly the case inlarger transport vehicles that have multiple heat exchangers in theinterior. For example, extended cab vehicles, large passenger vans, andmilitary tactical vehicles typically include two in-dash heatexchangers, two mid-cabin heat exchangers, and two rear cabin heatexchangers. The two heat exchangers are normally packaged together witha common blower in order to effectively and adequately heat or cool theentire interior. In some applications a large single interior heatexchanger is used while a high CFM blower forces the treated air viaductwork to multiple locations throughout the interior. This ductworkconsumes additional interior cabin space, requires the use ofinsulation, and must be sufficiently rigid so that it does not collapseor bend during the loading or unloading of personnel and cargo. It canbe seen that cost, weight, and space are all important concerns.

Yet another disadvantage of the conventional heating, cooling,ventilation system is that the engine of the vehicle must be running inorder to produce heat. Furthermore, there is usually some delay in theproduction of heat under cold weather starting conditions. Under theseconditions, the engine must first warm the engine coolant to anoperating temperature that is high enough (usually 150-210 deg F.) toproduce heated interior airflow from a coolant water to air heatexchanger. This delay in heat production can be inconvenient for thedriver and passengers in the cabin. Besides heating the vehicleinterior, the front windshield may also need to be heated or defrostedbefore the vehicle can be driven. In such cases, waiting for the engineto sufficiently warm to defrost the front windshield can increase thetime needed before the vehicle can be driven

Yet another disadvantage of a conventional heating, cooling, ventilationsystem is that the engine must be running to provide the mechanicalrotational energy for air conditioning compressor and engine water pumprotation. During times of loitering or silent watch, personnel mayremain inside the vehicle for safety and for protection against theoutdoor environment. When loitering or under silent watch, it isgenerally preferred that the engine be shut off. This loss of enginerotational energy for air conditioning and engine water pump operationstops interior heating, cooling and ventilation. During cold weatheroperation the interior can become as cold as the surrounding ambient.Cold weather clothing can help retain body heat but wearing suchclothing is both cumbersome and restrictive. Therefore, lack of heatwhen the engine is off can also be a problem.

In cold weather conditions, the interior vehicle temperature will rarelyif ever be lower than the exterior ambient temperature. On the otherhand, during hot weather conditions, the interior vehicle temperaturecan significantly exceed exterior ambient temperatures. The exteriorcolor of the vehicle, solar radiation entering through the windows ofthe vehicle, and additional heat load from the surrounding ground(radiating under and around the vehicle) all contribute to thetemperature rise inside the vehicle. In many instances personnel areunable to remove protective clothing to aid in reducing bodytemperature. As a result, the interior vehicle temperature can becomeextreme within minutes. Prolonged exposure to elevated temperatures cancause physical stress that ultimately impairs the ability of personnelto perform.

Yet another disadvantage of present conventional heating, cooling,ventilation systems is that fresh air filtration systems provide limitedprotection from harmful gasses and biological contaminants. In manycases carbon based filters and particulate filters are undersized forease of integration and to keep consumer costs low, and thus onlylimited protection is provided. In addition, airflow density andvelocity through the filters is not managed thus producing off gassingand reducing overall capacity.

Yet another disadvantage of present conventional heating, cooling, andventilation systems, particularly for military vehicles, is the use ofexternally mounted Nuclear, Biological, and Chemical (NBC) filtrationsystems. These filtration systems are intended to slightly overpressurize the vehicle interior. Current state of the art NBC filtrationsystems are self-contained and mounted outside of the vehicle. Thisapproach exposes the ventilation over pressurization system to heat andcold, increasing the load on the vehicle heating and cooling system. Inaddition, an exterior mounted system is outside of standard vehicleprotective armor and may require additional shielding or armor forprotection. This further contributes to vehicle weight, time required toservice the system, and mounting complexity. Another disadvantage of anexterior mounted system is that it provides additional surfaces whereweapons such as hand grenades could become stuck or lodged.

Yet another disadvantage of the conventional heating, cooling,ventilation system is that vehicle NBC ventilation over pressurizationsystems regulate the interior pressure of the vehicle by increasing ordecreasing the over pressurizing air flow. These systems do not monitorthe density or velocity of the air moving through an NBC filter system.As such, the particulate and vapor adsorbing ability of the filtersystem can be greatly reduced.

Yet another disadvantage of the conventional heating, cooling,ventilation system is the introduction into the vehicle interior ofexternal filtered over pressurization air. Current systems introduce thefiltered airflow directly into the interior or into the recirculationairflow of the heater/air conditioner. The method of mixing the ambientfiltered air flow before passing the ambient air through a heatexchanger is less efficient than introducing the ambient air directly tothe heat exchanger.

Yet another disadvantage of the conventional heating, cooling, andventilation system is the lack of airflow control for use with amilitary personnel cooling vest. During cooling vest operation, air flowfrom the heating, cooling, and ventilation system is used to provideheat transfer from a cooling vest heat exchanger to the fluid inside ofthe vest. The lack of a conditioned airflow control can impede theefficient operation of the cooling vest. As with a high interior vehicletemperature, insufficient vest cooling can cause physical stress thatultimately impairs the ability of personnel to perform.

For at least these reasons there is a need to provide a heating, coolingand ventilation system for a vehicle interior that is compact,effective, and concealed by protective armor (for military vehicles)while providing occupant comfort and safety during both engine on andoff conditions. The present invention therefore relates to an improveddesign for a heating, cooling and ventilation system for a vehicleinterior.

SUMMARY OF THE INVENTION

The invention may take form in certain structures and components,several embodiments of which will be described in detail in thisspecification and illustrated in the accompanying drawings. In thedrawings:

According to one aspect of the present invention, a heating, cooling,and ventilation system for an associated vehicle is provided. Theassociated vehicle includes a body and an engine. The body includes acabin defining an interior portion of the associated vehicle. The systemincludes a first refrigerant compressor selectively coupled to a shaftof the engine of the associated vehicle. The first compressor includesan inlet and an outlet. A second refrigerant compressor is selectivelyconnected to an electrical power source of the associated vehicle. Thesecond compressor includes an inlet and an outlet. A firstrefrigerant-to-air heat exchanger (RTAX) is provided in fluidcommunication with air in the interior portion of the associatedvehicle. A second RTAX is secured to the body of the associated vehicleand is in fluid communication with air exterior to the cabin of theassociated vehicle. A valve member includes a cooling position andheating position. The valve member operatively connects the inlets ofthe first and second compressors to a refrigerant outlet of the firstRTAX while connecting the outlets of the first and second compressors toa refrigerant inlet of the second RTAX when the valve member is in thecooling position. The valve member operatively connects the outlets ofthe first and second compressors to a refrigerant inlet of the firstRTAX while connecting the inlets of the first and second compressors toa refrigerant outlet of the second RTAX when the valve member is in theheating position. A blower is mounted to the associated vehicle and isconfigured to move air through the first RTAX. A controller is providedcapable of selectively activating one or more of the first compressorand the second compressor while placing the valve member into one of thecooling position and the heating position, based upon one or more systeminputs.

According to another aspect of the present invention, a method ofheating, cooling, and ventilating air in a cabin of a vehicle isprovided. The cabin defines an interior portion of the vehicle. Themethod includes providing a heating, cooling, and ventilation systemincluding a first refrigerant compressor selectively coupled to a firstpower source. A second refrigerant compressor is provided selectivelycoupled to a second power source. A first refrigerant-to-air heatexchanger (RTAX) is provided in fluid communication with air in thecabin of the vehicle and a second RTAX in fluid communication with airexterior to the cabin of the vehicle. The first and second RTAX are influid communication with the first and second compressors and arefrigerant valve member. The valve member including a cooling positionand heating position. A controller is provided in electricalcommunication with the first and second compressors, the valve member,and one or more system inputs. At least one of the first and secondcompressors is activated via the controller. Air in the cabin is heatedwhen the controller biases the valve member into the heating position,compressing and condensing a refrigerant in the first RTAX whileevaporating the refrigerant in the second RTAX and moving air in thecabin through the first RTAX. Air in the cabin is cooled when thecontroller biases the valve member into the cooling position,compressing and condensing the refrigerant in the second RTAX whileevaporating the refrigerant in the first RTAX, and moving air in thecabin through the first RTAX. At least one of the first compressor andthe second compressor is cycled and a temperature of the air in thecabin regulated via the controller based on one or more system inputs.

According to yet another aspect of the present invention, an airtreatment system for a vehicle includes a first compressor selectivelycoupled to a first power source of the vehicle. A second compressor isselectively coupled to a second power source of the vehicle. A firstheat exchanger communicating with an interior space is defined in thevehicle. A second heat exchanger communicates with an environmentexterior to the vehicle. A valve member is provided which, in a firstposition, couples an inlet of each of the first and second compressorsto an outlet of the first heat exchanger and an outlet of each of thefirst and second compressors to an inlet of the second heat exchanger.In a second position, the valve member couples the outlets of the firstand second compressors to an inlet of the first heat exchanger and theinlets of each of the first and second compressors to an outlet of thesecond heat exchanger. A controller is provided that selectivelyactuates at least one of the first and second compressors and the valvemember.

According to still yet another aspect of the present invention, an airtreatment system for a vehicle includes a refrigerant compressorselectively coupled to a first power source of the vehicle. A first heatexchanger communicates with an interior space defined in the vehicle. Asecond heat exchanger communicates with an environment exterior to thevehicle. A valve assembly is provided. In a first setting, the valveassembly couples an inlet of the refrigerant compressor to an outlet ofthe first heat exchanger and an outlet of the refrigerant compressor toan inlet of the second heat exchanger. In a second setting, the valveassembly couples the outlet of the refrigerant compressor to an inlet ofthe first heat exchanger and the inlet of the refrigerant compressor toan outlet of the second heat exchanger. A nuclear-biological-chemical(NBC) filtration unit is secured to the vehicle. The unit includes ablower, an inlet in fluid communication with air exterior to thevehicle, and an outlet in fluid communication with air in the interiorspace of the vehicle.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention may take form in certain structures and components,several embodiments of which will be described in detail in thisspecification and illustrated in the accompanying drawings. In thedrawings:

FIG. 1 is a schematic view of a first embodiment of a vehicle interiorheating, cooling, and ventilation (VIHCV) system according to thepresent invention.

FIG. 2 is an enlarged view of a forward portion of FIG. 1 more clearlyillustrating the VIHCV system.

FIG. 3A is a schematic view of FIG. 1 illustrating the VIHCV systemoperating in a cooling mode with a vehicle engine running.

FIG. 3B is a schematic view of FIG. 1 illustrating the VIHCV systemoperating in the cooling mode with the vehicle engine off.

FIG. 4A is a schematic view of FIG. 1 illustrating the VIHCV systemoperating in a heating mode with the vehicle engine running in ambientconditions greater than 40° F.

FIG. 4B is a schematic view of FIG. 1 illustrating the VIHCV systemoperating in the heating mode with the vehicle engine running in ambientconditions at or around −40° F.

FIG. 4C is a schematic view of FIG. 1 illustrating the VIHCV systemoperating in the heating mode with the vehicle engine running in whilethe engine coolant exit temperature is less than 80° F.

FIG. 4D is a schematic view of FIG. 1 illustrating the VIHCV systemoperating in the heating mode with the vehicle engine off.

FIG. 5 is a schematic view of a Nuclear, Biological, and Chemical (NBC)filtration unit of the VIHCV system.

DETAILED DESCRIPTION

With reference to FIGS. 1 and 2, a first embodiment of a vehicleinterior heating, cooling, and ventilation system (VIHCV) 10 is shown.Generally, the VIHCV system 10 is intended to be installed in a vehicle12. The vehicle 12 may be used for the transportation of militarypersonnel, civilians and/or cargo. In addition, the vehicle 12 may beconfigured as a fighting vehicle intended for tactical or combatmissions. Even still, the vehicle 12 could be an electric, hybridelectric (HEV), or alternative fuel driven vehicle. Typically, thevehicle 12 includes an engine compartment 14, an interior or cabin 16,an engine or other prime mover 18, a radiator 20, a radiator fan 22 anda set of wheels 24. Also, a pressurized Nuclear, Biological, andChemical (NBC) air filtration system 25 (FIG. 5) is supplied forcollective protection providing over pressurization of the interior ofthe vehicle.

With reference now to FIG. 2, the VIHCV system 10 generally includes afirst or primary compressor 26, an exterior heat exchanger 28, a firstor primary interior air handler or heat exchanger unit 30, a reversibleflow valve 32 or other flow switching means, a suction line accumulator34 and a series of refrigerant lines 36. The primary compressor 26 maybe of a fixed displacement type or of a variable displacement type.Having a variable displacement compressor may be preferred to moreefficiently manage the heating or cooling needs of the vehicle cabin,while rotating the compressor at a fixed speed. This may be preferred ifthe engine 18 of the vehicle 12 will remain idling or at high speed forextended periods of time.

As shown in FIG. 2, the primary interior heat exchanger unit 30 includesa refrigerant-to-air (RTA) type heat exchanger 30 a, a water-to-air(WTA) heat exchanger 30 b and a blower 30 c. The primary interior heatexchanger unit 30 and exterior heat exchanger 28 (shown in FIG. 2) arecommon in under dash automotive applications. Although, the WTA heatexchanger 30 b is shown in the disclosed embodiment of the VIHCV system10, it could be eliminated in various other contemplated embodiments. Aconduit of metal or hose may be provided to communicate with the outputairflow of the NBC filtration system 25 (FIG. 5). In addition, anon-filtered fresh air inlet with a damper door is provided in thepressurized air stream between the NBC filtration system 25 (FIG. 5) andthe primary interior heat exchanger unit 30. Depending on theapplication and nature of the vehicle, the heat exchangers may be madeof thicker gauge tubing and include a shock absorbent layer to make theexchangers more puncture and leak resistant.

A fin and tube, micro channel, fin and plate or any other state of theart coil design can be used for the heat exchangers. In particular, thecoil designs of the exterior heat exchangers and interior heatexchangers may incorporate wide fin spacing to allow dust and dirt topass through. The working fluid for the present invention can be anytype of known refrigerant suitable for heating and cooling applications.For example, SUVA® Hydro fluorocarbon (HFC) 134 a manufactured by theDupont Company, is a commonly used refrigerant.

The VIHCV system 10 includes various operating or climate controlstrategies for when the system is running in either a cooling mode or aheating mode. By way of example, each of FIGS. 3A-3B illustrate acontrol strategy, where the system 10 is operating in the cooling mode.Similarly, each of FIGS. 4A-4D illustrate a control strategy where thesystem 10, is operating in the heating mode. In addition, the VIHCVsystem 10 includes two modes of ventilation air flow, NBC filtered andnon-filtered. A dust filter element or a centrifugal dust separator orother mechanical separator can be integrated to the non NBC filteredventilation inlet air flow when used in desert or dusty conditions. Whenthe system 10 is operating in the cooling mode, heat is transferred or“pumped” from the interior 16 of the vehicle 12 to the outside. Theprimary difference between the cooling mode and the heating mode of thesystem 10 is based upon the direction in which the refrigerant isflowing. Generally, if the refrigerant is being compressed or condensedin or toward the exterior heat exchanger 28, then the system 10 isoperating in the cooling mode. On the other hand, if the refrigerant isbeing compressed or condensed in or toward the interior heat exchangerof the vehicle 30 a, then the system 10 is operating in the heatingmode. Compressing the refrigerant causes it to condense and, as therefrigerant undergoes this phase change, heat is produced. Conversely,expanding the refrigerant causes it to evaporate thereby absorbing heat.

The reversible flow valve serves to change or reverse the direction offlow of the refrigerant as between the interior and exterior heatexchangers 28,30 a, thus placing the system in either the heating modeor the cooling mode. With reference to FIG. 2, the reversible flow valve32 may include four ports A-D. When the reversible flow valve 32 is in acooling position, a first port A and a second port B are in fluidcommunication while a third port C and a fourth port D are in fluidcommunication. On the other hand, when the reversible flow valve 32 isin a heating position, the first port A and the third port C are influid communication while the second port B and the fourth port D are influid communication. The reversible flow valve 32 may be urged intoeither the cooling or heating positions, through the use of anelectromagnetic solenoid device, such that when current is applied, thevalve is held in one position or the other. When power to the valve isoff, it may be biased into the opposite position, for example, throughthe use of a spring or system pressure. A control signal for controllingthe heating or cooling operation of the system 10 may originate from avehicle environment controller 35, a controller area network buss, orother switching or control device located within the vehicle 12. Ofcourse, rather than using a self-contained reversible flow valve, anumber of separate valves could be connected and actuated in such amanner as to create the same flow reversing effect.

With continued reference to FIG. 2, the primary compressor 26 drawsrefrigerant through a primary suction port PS from the accumulator 34and pumps it out a primary discharge port PD. The accumulator 34 servesas a reservoir and settling tank for the refrigerant that flows backfrom the heat exchangers. Because the refrigerant undergoes a phasechange from the liquid state to the vapor state every time it cyclesthrough the system 10, it is possible that the refrigerant uponcompleting the cycle will contain entrained vapor bubbles. Typically,entrained vapor inhibits compressibility and can lead to damage or rapidwear-out of a compressor. The accumulator 34 will allow entrained vaporto settle out from the liquid refrigerant. After the refrigerant ispumped out of the discharge port PD of the primary compressor 26, itthen flows to the reversible flow valve 32 into the first port A. Whenin the cooling mode, the refrigerant is routed to the second port Bwhich eventually travels toward the exterior heat exchanger 28. Theexterior heat exchanger 28 includes two fluid ports, a first port E anda second port F. During cooling, compressed refrigerant flows into thefirst port E of the heat exchanger 28 dissipating heat and eventuallyflowing out the second port F. Adjacent to and in fluid communicationwith the second port F, is a first throttling or expansion member 37 a.In general, a throttling or expansion member is typically used toprovide some resistance or intermittent occlusion, to allow thecompressor in a refrigerant-based system to build pressure. Thethrottling member may involve the use of an electrically or mechanicallycontrolled valve, check valve, solenoid, or other selectivelyrestrictive device. In the instant embodiment, the first throttlingmember 37 a offers no restriction when operated in reverse flow (coolingmode), allowing the exterior heat exchanger 28 to act as a condenser.

As the primary compressor 26 pushes the refrigerant vapor through thedischarge port PD and towards the exterior heat exchanger 28, thepressure and temperature of the refrigerant will rise. After flowingthrough the exterior heat exchanger 28, chilled, yet high pressurerefrigerant flows towards the RTA heat exchanger 30 a. In addition, asecond throttling member 37 b can be located at a first port G of theinterior RTA heat exchanger 30 a in the primary interior heat exchangerunit 30. In the cooling mode, the second throttling member 37 b at thefirst port G remains at least partially occluded until the temperatureor pressure reaches a first threshold. Once the first threshold is met,the second throttling member 37 b opens allowing the refrigerant to flowand extract the maximum amount of heat from the interior or cabin 16. Athird additional throttling member 37 c is also illustrated in FIG. 2which will be discussed in greater detail below.

Still with reference to FIG. 2, as heat is transferred within theinterior heat exchanger unit 30 while in the cooling mode, therefrigerant flows through a second port H of the interior RTA heatexchanger 30 a and towards the third port C of the reversible flow valve32. Upon entering the reversible flow valve 32, the refrigerant isrouted from the third port C to the fourth port D and back to theaccumulator 34 where it is allowed to coalesce and once again be drawnout by the primary compressor 26. This cycle continues indefinitely,until the desired temperature of the cabin 16 is reached.

When the VIHCV system 10 is operating in the heating mode, thereversible flow valve 32 or flow switching means is in a positionopposite of the cooling mode position. As in the cooling mode, theprimary compressor 26 pumps refrigerant through the discharge port PDand towards the first port A of the reversible flow valve 32. However,instead of the refrigerant flowing from the first port A to the secondport B, it now, instead, flows from the first port A to the third portC. The refrigerant now travels from the third port C to the second portH of the interior RTA heat exchanger 30 a and through the primaryinterior heat exchanger unit 30. The RTA heat exchanger 30 a now acts asa condenser rather than an evaporator. As the refrigerant flows throughthe RTA heat exchanger 30 a, the refrigerant has no restriction due tothe reverse flow through the second throttling member 37 b locatedadjacent to and in fluid communication with the first port G and isinstead restricted by the first throttling member 37 a. As the primarycompressor 26 continues to run, the temperature and pressure of therefrigerant within the RTA heat exchanger 30 a begins to rise. Cabin airfrom the vehicle interior 16 is drawn into the heat exchanger unit 30and heated air is exhausted back into the interior 16. The firstthrottling member 37 a at second port F of the exterior heat exchanger28 restricts the refrigerant flow causing the exterior heat exchanger 28to function as an evaporator. As the refrigerant passes through theexterior heat exchanger 28, it absorbs heat from the environment andeventually exits through the first port E of the exterior heat exchanger28. The refrigerant then travels back to the reversible flow valve 32,entering through the second port B, exiting through the fourth port Dand returning to the accumulator 34.

The primary compressor 26, as illustrated in FIG. 3, is driven by theengine or prime mover 18 of the vehicle 12. The primary compressor 26may be either belt driven or directly coupled to a rotating shaft of theengine 18. Typically, an electrical clutch 38 is implemented to engageand disengage the primary compressor 26 from the engine 18. Anelectrical pulse may be generated from the instrument panel within thecabin 16 or from the vehicle environment controller 35 within thevehicle 12 to properly actuate or disconnect the primary compressor 26.During operation, if the suction side of the primary compressor 26reaches a predetermined low pressure, the compressor will be stopped bythe elimination of electrical power and/or decoupling from the engine18. The stopping of the primary compressor 26 will also occur if apredetermined high pressure is reached at the discharge port PD of thecompressor.

With continued reference to FIG. 2, another embodiment of a vehiclecabin heating and cooling system includes many of the same elements aspreviously described. However, either in addition to or in place of aprimary compressor 26, an alternate or secondary compressor 39 may beused. The secondary compressor 39 is effectively connected in parallelwith or in place of a primary compressor 26 via a secondary suction portSS and a secondary discharge port SD. The secondary compressor 39 isindependent from the engine 18 and can therefore provide compressedrefrigerant flow for heating and cooling of the vehicle 12 while theengine 18 is off. As shown in FIG. 2, the secondary compressor 39 isconnected in parallel with the primary compressor 26 and the secondarycompressor 39 is powered by direct current (DC) power supplied from oneor more on board batteries. As described with the primary compressor 26,the independent secondary compressor 39 may be a fixed displacementcompressor or a variable displacement type. The ability to adjust thevolume of refrigerant flow without shutting off the compressor reducesinrush current requirements on the electrical supply. And is moreefficient by matching the power demand of the compressor to the actualload. The compressor can be a variable speed, bypass or a digital scrolldesign.

In addition, a local power grid, external generator, or otheralternating current (AC) source can be used for extended operation ofthe VIHCV system. This may be accomplished through the use of aninverter or NATO slave cable. In this manner, the separate andindependent secondary compressor 39 provides for operating the heatingand cooling system, without producing any audible or visible signs ofthe vehicle 12 running. In other words, the vehicle can be manned in asilent mode for surveillance purposes or the like. When external poweris provided to the VIHCV system, it can continuously provide climatecontrol of the vehicle interior. There are several advantages to havingthe capability of operating on external power. For example, less fuel isconsumed and the interior can be pre-heated or pre-cooled before use. Inaddition, the vehicle can remain stationary (with the engine off) forindefinite periods of time while occupants or personnel of the vehiclecan comfortably remain inside while carrying on various tasks (e.g.,operating radios, computers, or other equipment).

As in the previous embodiments, the primary compressor or secondarycompressor may be actuated via the controller 35 of the system, athermostat or an instrument panel switch. In either case, the compressormay be commanded to run until the desired temperature is reached withinthe interior 16. The secondary compressor 39 may be used in conjunctionwith or in place of the primary compressor 26 to cause the refrigerantto compress more quickly, thus providing for a greater heat capacity(i.e. BTUs/hr).

With continued reference to FIG. 2, in yet another embodiment, the VIHCVsystem uses an auxiliary heating unit (AHU) 40. The AHU 40 is intendedto operate in very low outdoor temperature environments when engine 18is idling, off, or is otherwise incapable of producing enough heat forthe VIHCV system. The AHU 40 produces heated water using a heater 40 ato augment the heat from the engine water coolant. When operating theVIHCV system with the engine off, the AHU 40 may provide all of theheated water to a water-to-refrigerant (WTR) heat exchanger 42. The WTRheat exchanger 42 can be a heat exchanger having refrigerant flowingthrough one side of the heat exchanger (between a port I and a port J)and water flowing through the other side of the heat exchanger (asbetween ports L and N). The heat exchanger 42 can be a shell-in-tube,coaxial, brazed plate or any state of the art refrigerant heatexchanger. The AHU may include a port K for receiving engine watercoolant and a port L which serves as a heated water outlet. In one modeof operation, the AHU receives engine water coolant from a port M duringthe heating control schemes depicted in FIGS. 4C and 4D. The coolanteventually travels in through port K to absorb heat from the heater 40a, out port L and into the WTR heat exchanger 42. Simultaneously,refrigerant flows into port I at a low pressure and expands adsorbingheat from the engine coolant/water. Heated refrigerant then exits portJ, settles in the accumulator 34, and is again drawn out by thesecondary compressor 39 and/or the primary compressor 26. Thereafter,the compressed refrigerant travels via the reversing valve 32 to port Hof the interior RTA heat exchanger 30 a. During this process, theengine/water coolant in the WTR heat exchanger 42 is circulated throughthe WTA heat exchanger 30 b, where any residual heat is extracted intothe interior cabin and eventually returned back into the engine watercooling system through port N or, depending on the conditions,recirculated into the AHU via port K based on the position at watersolenoid valve 43.

Still with reference to FIG. 2, the heater 40 a may be designed to heatthe water surrounding the refrigerant line within the WTR heat exchanger42 or heat the refrigerant lines directly. This may be accomplished byusing a fuel burner for the heater 40 a that may consume either propane,CNG, kerosene, diesel, gasoline or any other combustible fuel source, togenerate a heat source within the AHU for heating the refrigerant. Theheater 40 a may even include an electrical resistance type element forheating the refrigerant. In either case, when the AHU 40 is operating,refrigerant is diverted away from the exterior heat exchanger 28 andtowards the WTR heat exchanger 42/AHU 40. This is accomplished byclosing a first valve 44 and opening a second valve 46. In addition, thethird throttling member 37 c may be located adjacent to and incommunication with port I of the WTR heat exchanger 42/AHU 40 to providethe maximum amount of heat transfer between the gas or water heat sourceand the refrigerant within the system 10.

Now with reference to FIG. 3A, the VIHCV system 10 is shown in thecooling mode with the engine 18 running. As indicated by thehighlighting and the modified line types of the refrigerant lines, therefrigerant is being pumped by the primary compressor 26 towards theexterior heat exchanger 28 where the refrigerant is condensed. Condensedrefrigerant travels to the second throttling member 37 b adjacent to theprimary interior heat exchanger unit 30 where the refrigerant is thenallowed to evaporate into the RTA heat exchanger 30 a. The refrigerantthen flows back to the reversible valve 32 and back into the primarysuction port PS of the primary compressor 26.

By comparison, FIG. 3B illustrates the VIHCV system 10 operating in thecooling mode while the engine 18 is off. In this case, the operation ofthe cooling system is identical to the operation as discussed withreference to FIG. 3A. However, now the secondary compressor 39 isoperating in place of the primary compressor 26. As discussedpreviously, the secondary compressor 39 is electrically driven and maybe operated by a variety of internal or external electrical powersources.

Now with reference to FIGS. 4A-4D, the VIHCV system 10 illustratesvarious operating scenarios while operating in the heating mode. Forexample, FIG. 4A illustrates the system 10 producing heat in theinterior 16 of the vehicle 12, while the engine 18 is running and whilethe exterior ambient conditions are greater than 40° F. In thisparticular scenario, the engine driven primary compressor 26 deliversrefrigerant to be condensed in the RTA heat exchanger 30 a. Eventually,the refrigerant passes through the second throttling 37 b member and therefrigerant passes to the exterior heat exchanger 28, where heattransfer occurs between the refrigerant and the ambient outdoorenvironment. This scenario optimizes the efficiency of the heatingsystem but, depending on the insulation characteristics of the vehicle12, may only produce enough heat when the ambient conditions are greaterthan 40° F. or during prolonged engine idling conditions.

When ambient temperatures fall below 40° F., an additional heat sourcemay be required to supplement the heat capacity of the system 10,particularly if the engine 18 is cold. This scenario is illustrated byFIG. 4B. In this case, the alternate heating unit (AHU) 40 provides thesupplemental heat. Heat is initially transferred from the alternateheating unit to a closed loop water system which circulates between theAHU 40 through the WTR heat exchanger 42. The water eventually flowsinto the WTA heat exchanger 30 b and finally returns back to the AHU 40.The WTR heat exchanger 42 transfers the heat from the heated coolantwater to the refrigerant flowing from the RTA heat exchanger 30 a. Thisrefrigerant then flows through the third throttling member 37 c into therefrigerant side of the WTR heat exchanger 42 and finally returns to thesuction line accumulator 34. The refrigerant is then drawn out of theaccumulator 34 and into the suction port PS by the primary compressor26. As indicated by the lack of shading in the exterior heat exchanger28, there is no refrigerant flow through the exterior heat exchanger 28.In effect, the WTR heat exchanger 42 has replaced or circumvented theexterior heat exchanger 28. In order to put the system 10 into thisoperating scenario, the water temperature solenoid valve 43 and therefrigerant valve 44 must be closed, while the refrigerant valve 46 ispermitted to open. The ability to circumvent the exterior heat exchanger28 has at least two advantages. One is during the heat pump mode theexterior heat exchanger 28 does not need to be used to extract heat fromthe prevailing ambient air temperature that can become very inefficientas ambient temperatures become colder. The WTR heat exchanger 42 is usedas the heat source and is not ambient air temperature dependent, andsecond if the exterior heat exchanger 28 would be used (as in currentambient air heat pump designs) the coil will have the tendency to sweator condensate water due to its colder than ambient air temperature.Sweating or condensate in a vehicle application provides a wettingsource which promotes road dust and debris accumulation in these areas.This accumulation can result in a paste or mud that will adhere to thecoils of the heat exchangers, inhibit air flow, and reduce theperformance of the heat exchanger.

Now with reference to FIG. 4C, an operating scenario similar to FIG. 4Bis shown. However, the distinction is that the water temperature valve43 is permitted to flow water coolant back to the engine 18, as well asto the alternate heating unit 40. This scenario may be effective eitherwhen the engine coolant exit temperature is less than 80° F., such thatthe alternate heating unit 40 will be activated in order to acceleratethe warm up period of the engine 18. In addition, this scenario mayexist when engine 18 has reached its operating temperature and can nowaugment the heating capacity of the AHU 40, the WTR heat exchanger 42,and/or the interior RTA heat exchanger 30 a.

With reference to FIG. 4D, a heating mode scenario is shown with theengine 18 in the off state. In this case, engine coolant water iscirculated from the engine to the AHU 40, through the WTR heat exchanger42, through the WTA heat exchanger 30 b and back to the engine 18. Inaddition, the secondary compressor 39 is operating since the enginedriven primary compressor 26 is not. With the engine 18 off, thesecondary compressor 39 can operate the air conditioning system in a“heat pump” mode, similar to a home heat pump. The difference is thatinstead of ambient air or geothermal coils serving as a source of heat,the auxiliary heating unit 40 will be the heat source. This scenario ismost likely to be used under conditions where the engine is not runningand where it is preferable to maintain the engine at a certaintemperature, in the event a quick departure without engine hesitation orstart up issues would be required.

Now with reference again to FIG. 1, the first embodiment may include aplurality of secondary heat exchanger units 48 within the interior 16 ofthe vehicle 12. Specifically, one secondary interior heat exchanger unit48 is shown positioned toward the middle of the interior 16 and anothersecondary interior heat exchanger unit 48 is shown positioned towardsthe rear of the cabin 16. The secondary interior heat exchanger units 48are integrated into the VIHCV system 10 in a similar manner as theprimary interior heat exchanger unit 30. In fact, only three connectionsare necessary to fully integrate the secondary interior heat exchangers48 into the VIHCV system 10. These connections are indicated byreference signs O, P and Q as shown on FIGS. 1-2. In addition, thesecondary interior heat exchanger units 48 may be selectively integratedinto the VIHCV system 10 by simply actuating a third valve 50. When thethird valve 50 is actuated, refrigerant is allowed to flow through thethird valve 50, either to the heat exchangers 48 (as during cooling), orfrom the heat exchangers 48 (as during heating). The heat exchangers 48also include two ports each. As before, a throttling member is connectedadjacent each secondary heat exchanger unit 48 to extract the maximumamount of heat from the cabin as required. It should also be noted thatin addition to or in place of the secondary heat exchanger units 48personal cooling and heating vests may be worn by the occupants of thevehicle 12. These cooling vests may include connections for allowingthem to be selectively integrated with the remainder of the VIHCV system10. The connections points for the cooling vests would be similar to theconnections O, P, and Q as shown in FIGS. 1 and 2.

It should be noted that several combinations of different fluid typeheat exchangers could be used in the VIHCV system. For example, theprimary or secondary interior heat exchanger units may only include awater-to-air heat exchanger or only a refrigerant-to-air exchanger, orboth. It should also be noted that any combination of compressors may beused to compress the refrigerant during heating or cooling. In otherwords, the primary compressor and secondary compressor may work intandem, or independently from one another. In particular, as to heating,the alternate heating unit (AHU) may operate independently or incombination with either one or both of the primary and secondarycompressors. In addition, the AHU may heat the refrigerant directlyusing heated gas or via a secondary fluid such as engine coolant.

Lastly, FIG. 5 illustrates the Nuclear, Biological, and Chemical (NBC)filtration system 25 provided in the VIHCV system. The filtration system25 generally includes a damper 52, an NBC filter assembly 56, a blower60, and a pre-filter 62. The system 25 provides filtered pressurizedairflow to the interior of the vehicle. During filtered pressurizedairflow, the vehicle would be considered in a collective protectionconfiguration. The primary interior heat exchanger unit 30 communicateswith the airflow of the NBC filtration system 25. Airflow from 25 isintroduced directly into the heat exchangers of the primary interiorheat exchanger unit 30 providing the highest delta temperature to coils30 a and 30 b.

Some NBC protection applications may necessitate that the airflow fromthe filtration system 25 be discharged directly into the crewcompartment or cabin due to other vehicle component space issues, inthis case a pre-filter heat exchanger 57 can be placed prior to orintegrated within the housing of the NBC filter 56. The pre-filter heatexchanger 57 may be incorporated when optimum chemical filtration isrequired. The pre-filter heat exchanger 57 can be further used tocontrol the temperature and/or the relative humidity level of theincoming unfiltered air prior to the NBC filter assembly 56. Non-NBCfiltered outside airflow can be turned on or off and is controlled by adamper door 52 or other simple means. Naturally, placing the damper 52in an open or non-NBC filtered position will extend the life of thefilter 56. During collective protection or NBC filtration, damper 52 isclosed. In addition, the damper 52 is located downstream of thefiltration blower 60 such that if a leak exists in the damper 52, cleanfiltered air will leak to the outside. The outside air can be filteredby an NBC filter assembly 56 to different levels of protection dependingupon the threat level of vehicle operation by the use of different NBCor filter types.

The filter assembly 56 can be one larger filter, a package of individualsmaller filters or be separate filters housed within a protective sleeveor shell 58. The NBC filter assembly 56 can comprise of a gas phase andparticulate filter as one unit or the gas phase filter can be separatefrom the particulate filter to provide better integration within thevehicle 10 (FIG. 1). In addition, the filters of the NBC filter assembly56 may be of the regenerative type such that the filters can be heated(using refrigerant or engine coolant of the VIHCV system) and reverseblown to expel trapped contaminants, thus, restoring/extending filtercapability/life. When individual gas phase filters are required forspace savings the filters are housed inside the protective sleeve 58.The protective sleeve may be one or more metal tubes designed to hold agas phase filter and or particulate filter. The tubes can be located inareas of the vehicle that are armor protected, but provide enough openarea to mount the filter tubes without loss of cargo or crew space. Theability to use different sizes and shapes of filters will facilitateease of installation, provide the highest level of gas and particulateprotection, while protected inside the vehicle and/or by armor. Filterassembly 56 and filtration blower 60 are protected from ingestion ofsand and dust by a self-cleaning pre filter 62. The self-cleaning prefilter 62 can be a sand trap consisting of metal baffles or a highefficiency mechanical or non mechanical cyclonic separator.

During collective protection mode or NBC operation, the interior andfiltration system 25 provide for a slightly higher pressure inside thecabin as compared to outside the cabin. This slight positive cabinpressure ensures that contaminants, toxins, or chemicals will not enterthe cabin via small openings or leaks within the interior of thevehicle. When the filtration system 25 is operating, the vehicleenvironment controller 35 (FIG. 2) can also monitor the specific cubicfeet per minute (SCFM) flow rate of the air through the filters 56 aswell as cabin air pressure to ensure the best flow velocity through thefilter.

Several exemplary embodiments have thus been described. Modificationsand alterations may occur to others upon reading and understanding thepreceding detailed description. It is intended that the exemplaryembodiments be construed as including all such modifications andalterations insofar as they come within the scope of the appended claimsor the equivalents thereof.

The invention claimed is:
 1. A heating, cooling, and ventilation systemfor an associated vehicle, the associated vehicle including a body andan engine, the body including a cabin defining an interior portion ofthe associated vehicle, the system comprising: a first refrigerantcompressor selectively coupled to a shaft of the engine of theassociated vehicle, the first compressor including an inlet and anoutlet; a second refrigerant compressor selectively connected to anelectrical power source of the associated vehicle, the second compressorincluding an inlet and an outlet; a first refrigerant-to-air heatexchanger (RTAX) in fluid communication with air in the interior portionof the associated vehicle; a second RTAX secured to the body of theassociated vehicle and in fluid communication with air exterior to thecabin of the associated vehicle; a valve member including a coolingposition and heating position, the valve member operatively connectingthe inlets of the first and second compressors to a refrigerant outletof the first RTAX while connecting the outlets of the first and secondcompressors to a refrigerant inlet of the second RTAX when the valvemember is in the cooling position, the valve member operativelyconnecting the outlets of the first and second compressors to arefrigerant inlet of the first RTAX while connecting the inlets of thefirst and second compressors to a refrigerant outlet of the second RTAXwhen the valve member is in the heating position; a blower mounted tothe associated vehicle and configured to move air through the firstRTAX; a nuclear-biological-chemical (NBC) filtration unit secured to theassociated vehicle and in fluid communication with air exterior to thecabin of the associated vehicle; and a controller capable of selectivelyactivating one or more of the first compressor and the second compressorwhile placing the valve member into one of the cooling position and theheating position, based upon one or more system inputs.
 2. The system ofclaim 1, wherein the system inputs include one or more of an input froman ambient temperature sensor, an input from a cabin interiortemperature sensor, a target interior cabin temperature, and an inputfrom an engine coolant temperature sensor.
 3. The system of claim 1,wherein the first compressor or the second compressor include a variabledisplacement, scroll bypass, or digital scroll compression chamber. 4.The system of claim 3, wherein the controller is capable of varying adisplacement of the compression chamber of the first compressor or thesecond compressor.
 5. The system of claim 1, wherein the blower includesa first inlet for receiving an exterior ambient air flow and a secondinlet for receiving an interior cabin air flow.
 6. The system of claim1, wherein an outlet of the NBC filtration unit is in fluidcommunication with an inlet of the blower.
 7. The system of claim 1,wherein the NBC filtration unit includes a pre-filter heat exchanger. 8.The system of claim 1, wherein the NBC filtration unit includes areverse airflow regenerative filter.
 9. A heating, cooling, andventilation system for an associated vehicle, the associated vehicleincluding a body and an engine, the body including a cabin defining aninterior portion of the associated vehicle, the system comprising: afirst refrigerant compressor selectively coupled to a shaft of theengine of he associated vehicle, the first compressor including an inletand an outlet; a second refrigerant compressor selectively connected toan electrical power source of the associated vehicle, the secondcompressor including an inlet and an outlet; a first refrigerant-to-airheat exchanger (RTAX) in fluid communication with air in the interiorportion of the associated vehicle; a second RTAX secured to the body ofthe associated vehicle and in fluid communication with air exterior tothe cabin of the associated vehicle; a valve member including a coolingposition and heating position, the valve member operatively connectingthe inlets of the first and second compressors to a refrigerant outletof the first RTAX while connecting the outlets of the first and secondcompressors to a refrigerant inlet of the second RTAX when the valvemember is in the cooling position, the valve member operativelyconnecting the outlets of the first and second compressors to arefrigerant inlet of the first RTAX while connecting the inlets of thefirst and second compressors to a refrigerant outlet of the second RTAXwhen the valve member is in the heating position; a blower mounted tothe associated vehicle and configured to move air through the firstRTAX; a water-to-refrigerant heat exchanger (WTRX) having a refrigerantportion and an engine coolant portion, the refrigerant portion of theWTRX being in selective fluid communication with one or more of theinlet of the first compressor, the inlet of the second compressor, andthe refrigerant outlet of the first RTAX, the engine coolant portion ofthe WTRX being in selective fluid communication with an engine coolantcircuit of the engine; and a controller capable of selectivelyactivating one or more of the first compressor and the second compressorwhile placing the valve member into one of the cooling position and theheating position, based upon one or more system inputs.
 10. The systemof claim 9, wherein the controller is capable of placing the WTRX intofluid communication with the first RTAX and the engine coolant circuitwhen an ambient temperature is below a first threshold.
 11. The systemof claim 9, further including an auxiliary heating unit (AHU) in fluidcommunication with one or more of the engine coolant circuit and theWTRX.
 12. The system of claim 11, wherein the controller is capable ofactivating the AHU thereby providing heat to one or more of the enginecoolant circuit and the WTRX when an ambient temperature is below asecond threshold.
 13. The system of claim 9, wherein the system inputsinclude one or more of an input from an ambient temperature sensor, aninput from a cabin interior temperature sensor, a target interior cabintemperature, and an input from an engine coolant temperature sensor. 14.The system of claim 9, wherein the first compressor or the secondcompressor include a variable displacement, scroll bypass, or digitalscroll compression chamber.
 15. The system of claim 14, wherein thecontroller is capable of varying a displacement of the compressionchamber of the first compressor or the second compressor.
 16. The systemof claim 9, wherein the blower includes a first inlet for receiving anexterior ambient air flow and a second inlet for receiving an interiorcabin air flow.
 17. The system of claim 9, further including anuclear-biological-chemical (NBC) filtration unit secured to theassociated vehicle and in fluid communication with air exterior to thecabin of the associated vehicle.
 18. The system of claim 17, wherein anoutlet of the NBC filtration unit is in fluid communication with aninlet of the blower.
 19. The system of claim 17, wherein the NBCfiltration unit includes a pre-filter heat exchanger.
 20. The system ofclaim 17, wherein the NBC filtration unit includes a reverse airflowregenerative filter.
 21. The system of claim 1, further including awater-to-refrigerant heat exchanger (WTRX) having a refrigerant portionand an engine coolant portion, the refrigerant portion of the WTRX beingin selective fluid communication with one or more of the inlet of thefirst compressor, the inlet of the second compressor, and therefrigerant outlet of the first RTAX, the engine coolant portion of theWTRX being in selective fluid communication with an engine coolantcircuit of the engine.
 22. The system of claim 21, wherein thecontroller is capable of placing the WTRX into fluid communication withthe first RTAX and the engine coolant circuit when an ambienttemperature is below a first threshold.
 23. The system of claim 21,further including an auxiliary heating unit (AHU) in fluid communicationwith one or more of the engine coolant circuit and the WTRX.
 24. Thesystem of claim 23, wherein the controller is capable of activating theAHU thereby providing heat to one or more of the engine coolant circuitand the WTRX when an ambient temperature is below a second threshold.